TWI611980B - Gear arrangement - Google Patents

Abstract

A gear device for a system in which a guiding force is eccentrically introduced into a main shaft (1) of the gear device, the main shaft (1) included in the gear device is supported by a spindle bearing (3) Mounted rotatably relative to a stationary housing (2), wherein a sun gear (4) is disposed concentrically with the spindle (1), securely coupled to the housing (2), and includes a housing ( 2) rotating at least one control housing (5), the first portion (6) of which is coupled to the main shaft (1) in a torsionally resistant manner, rotatably mounted to the control by a first rotary bearing (10) The second portion (7) of the housing (5) is a planetary gear (8) that meshes with the sun gear (4), wherein a force transmitting device (9) is fixed to the control housing (5). A drive crank (11) is rigidly engaged with the planet gear (8) by a first end (12), wherein a second end (13) of the drive crank (11) is mounted in a rotational engagement On a crank arm (14), the crank arm (14) is supported by a movable coupling (15) relative to the control housing (5).

The present invention is based on the object of providing a gear unit that exhibits the most compact structural dimensions in the direction of the main shaft (1).

The object of the invention can be achieved by the fact that the movable coupling means (15) is a linear guide (16) which absorbs the tilting moment transmitted by the crank arm (14).

Description

Gear device

The present invention relates to a gear arrangement that is based on the features set forth in the preamble of claim 1.

Such a gear arrangement can, in particular, be mounted on a bicycle and provide an increase in this torque due to the introduction of power by the rider. In the present patent application, the housing of the gear unit is adapted to be part of a frame, and the force transmission device, such as, for example, a sprocket, transmits the torque generated by the rider through a chain to the rear wheel. The gear arrangement according to the invention, however, by way of example, may be arranged above a wind power generation system having a rotating vertical axis.

DE 10 2010 033 211 B4 discloses a bicycle gear device having a sun gear, a planetary gear, and a drive crank disposed in a common crankcase, while the crank arm is supported on a guide rail using a guide roller device, The configuration appears in the crankcase. The drive crank engages at both ends on a crank arm of the crank arm, in which case any tilting moment that may occur is absorbed. Conversely, the guide roller is free to run on the guide rail, otherwise the bearing assembly of the crank arm head will be subjected to excessive stress. A known disadvantage of using existing gear arrangements is that because of the free running guide roller, the 蹬 The step is seen as a "sponge" and, in addition, the known design of a crank arm mounted on the bearings at both ends will result in a high Q factor. The Q factor indicates the lateral spacing between the outer surfaces of the two pedal cranks in a bicycle. The larger the Q factor, the more the pedals are separated from each other. In the case of a sharp turn, the speed limit is imposed on it, which increases the risk of the pedal inside the turn coming into contact with the ground. At the same time, from an ergonomic point of view, a too high Q factor is harmful to health. In other areas of the art, it is also advantageous to be able to provide a gear unit of the most compact design in the direction of the spindle axis.

Accordingly, it is an object of the present invention to provide a gear arrangement that exhibits the most compact structural dimensions in the direction of the spindle axis.

The object of the invention can be achieved by the characterizing feature of claim 1.

The term "linear guide" is understood to mean a machine element that allows for the most frictionless translation of one or more movable modules in a machine while ensuring the direction of motion of a linear track. maintain. In this case, the linear guide according to the invention must also be able to absorb the tilting moment that occurs. Components that involve torque transfer, such as crank arms and drive cranks, do not change their length in this case, but only the pivots abut each other. The bearing axes of all rotatable mounting assemblies are parallel to each other.

Advantageously, the control housing includes a wall portion that faces the sun gear and the planet gears, and the outer side of the wall portion faces the drive crank. The wall portion forms a substantially flat plate, wherein the outer side surface It is arranged opposite to the inner side. Due to the wall, the sun gear and the planet gear are separated from the drive crank. As a result, these will facilitate protection from external influences, wherein in addition a package of the sun gear and planet gears can be engaged on the wall. The wall simultaneously carries the planet gears, which run completely through the wall in the axial direction.

According to another preferred embodiment, the crank arm is mounted on the drive crank by a second rotary bearing while being in contact with one end of the drive crank. This type of mounting will facilitate the compact size of the gear unit, since the drive crank can be mounted on one end of the crank arm so that no fork brackets are required on the bearings at the ends of the crank arms.

In terms of purpose, the linear guide is disposed outside the wall. Thus, the linear guide rotates with the control housing and maintains the same position relative to the force transfer device. The position of the linear guide on the outer side of the wall additionally contributes to the gear unit being as thin as possible in the direction of the spindle axis.

The force transfer device can be at least one sprocket. In the case of a transmission gear of a bicycle, it is also possible for a plurality of sprocket wheels of different diameters to be staggered with each other in the axial direction. As a sprocket replacement, a pulley or the like can also be used.

Advantageously, the linear guide comprises at least one rail and a slide guided thereon. The term "rail" is understood to mean a linear bearing and guiding element that is arranged, either individually or in pairs, parallel to each other. The slider, when in operation, is coupled to at least one rail in a non-detachable manner and guided thereon.

It has proven to be particularly advantageous if the at least one rail and/or the slide overlaps the sprocket at least in part in its axial direction or in the direction of the sun gear. In this case, the guide rail and/or the slider project into the at least one sprocket in the axial direction, with the result that the size of the gear device can be further reduced in the direction of the spindle axis.

As an alternative or in addition to the foregoing embodiment, the at least one rail may be configured in such a manner that a rotation of the crank arm causes a portion of the slider to travel twice on an intermediate shaft of the main shaft. The slider or at least a portion of the slider, thus, alternates about a central axis extending from the spindle. The result of the available travel path of the slider on the rail is that it can be moved into a central region of the sprocket. This embodiment helps the rail to also move in the axial direction and into the sprocket.

According to a first preferred embodiment, the track member includes a rail and the sliding member includes a slider, wherein the slider is movable on the rail in one degree of freedom. The term "degree of freedom" is defined as the number of movement possibilities of a system, which are independent of each other and are freely selectable in this sense. A rigid body can be moved (translated) in three mutually independent directions in space and can be rotated (swirled) in three mutually independent planes. In this embodiment, the slider can only move along the guide rail.

According to a second alternative embodiment, the track element comprises two rails and the sliding element comprises a slider, wherein the slider is movable on the rail in one degree of freedom. Due to the use of two parallel running rails, the risk of blockage or tilting is greatly reduced.

Preferably, the slider is disposed between the rails, and in each case the slider is supported by two pairs of rollers, wherein the pair of rollers in the general case comprises two rollers, the cross-sectional profile of which is shaped as Complementary to the cross-sectional profile of the associated rail. Typically, the rollers are configured to have a convex or concave cross-sectional profile. Due to the side-by-side mounting of the two rolls in each case, the tilting moment of the slide is effectively absorbed.

With the two embodiments described above, a third rotary bearing is advantageously directly engaged on the slider and the crank arm. Due to a rotational movement of the end of the crank arm engaged to the drive crank, the angular position of the entire crank arm is constantly changed relative to the slider during operation. With the aid of the third rotary bearing, the slider is detached from the angular position change of the crank arm.

According to a third alternative embodiment, two rails and two sliders are provided, one of which is fixed to each rail.

Each slider can be, in this case moving on the associated rail with one degree of freedom. This means that each of the sliders is guided on its associated rail in an anti-twist manner.

This is achieved, for example, by the fact that the guide rail and the slider exhibit a complementary shaped polygonal profile. In particular, a non-blocking operation can be achieved with a polygonal profile.

Each of the sliders is movable on the associated rail in two degrees of freedom. In this case, the sliders are guided on their associated rails and thus have the ability to rotate in the circumferential direction, i.e., the sliders are seated on a cylindrical rail.

Since in each case the two slides are used on an associated rail, the sliders can be connected to each other by means of a transverse element, while the third rotary bearing can be arranged between the transverse element and the crank arm. Due to the fixed connection by one of the transverse elements between the sliders, the sliders support and block each other to counter the rotation of the opposing rails.

Preferably, the (equal) slider is configured to linearly guide a spherical ring member or a slider bearing member. The linear spherical ring member is a ball bearing having a ball ring motion in an axial direction. The purpose of this linear guiding spherical ring element is different from the mounting of a rotating element of all other roller bearings, but rather allows a machine element to move along a straight line of the guide rail, i.e., translate, whereby the lowest friction can be guided. The linearly guided spherical annular element exhibits a lower frictional loss than an equivalent load sliding bearing.

In particular, when a gear unit is mounted on a bicycle, it is purposeful if the two control housings are engaged on the main shaft, wherein they are arranged 180 degrees apart from one another.

1‧‧‧ spindle

2‧‧‧Shell

3‧‧‧ spindle bearing

4‧‧‧Sun gear

5‧‧‧Control housing

6‧‧‧Control housing part 1

7‧‧‧Control housing second part

8‧‧‧ planetary gear

9‧‧‧Power transmission device

10‧‧‧First rotary bearing

11‧‧‧ Drive crank

12‧‧‧ drive crank first end

13‧‧‧ drive crank second end

14‧‧‧ crank arm

15‧‧‧ movable coupling

16‧‧‧Linear Guides

17‧‧‧ wall

17a‧‧‧ inside the wall

17b‧‧‧ outside the wall

18‧‧‧Second rotary bearing

19‧‧‧Sprocket

20‧‧‧Installation board

21‧‧‧Sliding arm

22‧‧‧ Third rotary bearing

23‧‧‧ rails

24‧‧‧Sliding parts

25‧‧‧First roll pair

26‧‧‧Second roller pair

27‧‧‧First roll

28‧‧‧second roll

29‧‧‧Transverse elements

30‧‧‧ pedal

31‧‧‧Retaining components

x‧‧‧Axis

For a better understanding, the invention will be described in more detail below in seven figures. These figures are:

Figure 1 is a perspective view of a gear device having two control housings; Figure 2 shows a cross-sectional view of the gear unit.

Figure 3 is a side elevational view of a linear guide of a gear unit according to a first embodiment.

Figure 4 is a perspective view of a linear guide of a gear unit according to a second embodiment.

Figure 5 is a side elevational view of a linear guide of a gear unit according to a third embodiment.

Figure 6 is a side elevational view of a linear guide of a gear unit according to a fourth embodiment.

Figure 7 passes through a cross-sectional view of the linear guide along the plane AA of Figure 6.

Figure 1 shows a perspective view of the gear unit according to the invention, which can be attached to a frame or carrier by a housing 2, not shown. The gear unit is configured to be mirror-symmetrical to both sides of the housing 2 except for the difference: at a portion on the front side of the plane of the drawing, a force transmission device 9 in the form of a sprocket 19 is provided. It is connected to a control housing 5 in a twist-resistant manner. On the sprocket 19, for example, a chain (not shown) can be arranged to sequentially transmit the rotational movement of the control housing 5 and thus the sprocket 19.

As shown in the section in Fig. 2, a spindle 1 extends through the housing 2, which is rotatably mounted relative to the housing 2 by means of two spindle bearings 3 which are mutually axially oriented Set apart from a distance. The spindle 1, in each case, is firmly connected to a control housing 5 at both ends.

Further, in each case, fixed to the opposite ends of the casing 2 is the sun gear 4. The two sun gears 4 coaxially surround the main shaft 1.

The control housing 5 is firmly connected to the main shaft 1 with its first portion 6 and is rotated about an intermediate axis x of the main shaft 1 by the drive of two crank arms 14 or one of the crank arms 14. In the control case In a second portion 7 of the body 5 opposite to the first portion 6, a planetary gear 8 is rotatably mounted by a first rotary bearing 10, and the planetary gear 8 is operatively engaged with the sun gear 4, and When the crank arms 14 are actuated, the planet gears are running thereon. The planet gear 8 projects completely through the second portion 7 of the control housing 5 in the direction of its axis extension. Rigidly fixed to the side of the planet gear 8 facing away from the housing 2 is a first end 12 of a drive crank 11 such that the drive crank 11 rotates with the planet gear 8 about a common axis. The crank arm 14 drives the drive crank 11 by a second rotary bearing 18 mounted on a second end 13.

The crank arm 14 is mounted on the bearing only on the side facing the control housing 5.

In addition to this, the crank arm 14 is rotatably supported by a third rotary bearing 22 on a movable coupling 15 in the form of a linear guide 16. The linear guide 16 is centrally mounted within the sprocket 19 and allows the crank arm 14 to move in a straight line at twice the radius of the crank 11 that is driven.

The control housing 5 comprises at least one wall portion 17 substantially perpendicular to the intermediate axis x, the inner side surface 17a of which faces the sun gear 4 and the planet gears 8. The opposite outer side surface 17b of the wall portion 17 is disposed adjacent to the drive crank 11 and the crank arm 14. In addition, the wall portion 17 carries the linear guide 16 on its outer side surface 17b, including at least one guide rail 23 regardless of its specific configuration. The at least one guide rail 23 is fixed at a fixed position on the outer side surface 17b of the wall portion 17 of the control housing 5, in particular using a threaded connection or a riveting.

Mounted on the ends of the two crank arms 14 in Fig. 2 are, for example, pedals 30, each pointing away from the gear unit.

Figures 3 through 7 illustrate different embodiments of linear guides 16 disposed in the gear arrangement in accordance with the present invention.

Figure 3 shows a first embodiment of a suitable linear guide 16 having a single rail 23 and a single slider 24 disposed thereon. The guide rail 23 is shaped and partially engaged with the slider 24 at the rear to effectively prevent the slider 24 from being disengaged from the plane of the drawing. The slider 24 has a degree of freedom with respect to the guide rail 23.

The rail 23 is located on a mounting plate 20 and is permanently connected thereto.

A slide arm 21 is formed on the slider 24, and on the end of the slider 24 facing away from the guide rail 23, the slide arm 21 extends to the third rotary bearing 22. Depending on the drive crank 11, the slide arms 21 are arranged obliquely to the crank arms 14. As shown in Fig. 3, the drive crank 11 and the crank arm 14 are aligned on a horizontal axis, so that maximum torque can be generated.

Figure 4 shows an alternative embodiment in which a slider 24 is held between two parallel rails 23 and guided in its axial direction. The slider 24 includes a first roller pair 25 facing the rail 23 on one side and a second roller pair 26 also adjacent the other rail 23 on the other side. The two roller pairs 25, 26 each have a first roller 27 and a second roller 28.

The guide rails 23 are configured to have a convex cross section on the side faces facing each other, the peripheral wall shapes being concave and the rollers 27 and 28 running thereon. In the same way, the guide rails 23 can be presented within one The cross section is concave, and the rolls 27, 28 can be configured to have a convex cross section.

A third rotary bearing 22 is visible centrally in the slider 24, through which the slider 24 is rotatably coupled to the crank arm 14.

By the two rollers 27, 28 disposed before and after the roller pair 25, 26, the slider 24 is prevented from tilting about the third rotary bearing 22. The slider 24, according to Fig. 4, also shows only one degree of freedom.

Fig. 5 shows another embodiment which is similar in principle to the embodiment in Fig. 3. However, as a difference, the two parallel rails 23 are fixed to the mounting plate 20, and the sliders 24 are located on each of the guide rails 23. Positioned on one of the ends of the guide rails 23, the first rotary bearing 10 is disposed therebetween.

The two sliding members 24 each include a sliding arm 21 extending obliquely to the direction of the crank arm 14, wherein the two sliding arms 21 are coupled to a transverse member 29. The third rotary bearing 22 is arranged in the region of the transverse element 29. Each slider 24 can be moved relative to the associated rail 23 with one degree of freedom.

Fig. 6 and Fig. 7 show another embodiment in which two cylindrical guide rails 23 are provided, on each of which a slider 24 is pressed. By means of the retaining element 31, the rails 23 are fixed at a distance from the mounting plate 20 and are completely surrounded in the circumferential direction by the sliders 24 guided thereon. Therefore, each slider 24 independently has two degrees of freedom. However, the transverse element 29 connects the two sliders 24, thereby preventing the respective sliders 24 from rotating about the respective rails 23. Here, the third rotary bearing 22 is also disposed between the transverse member 29 and the crank arm 14.

2‧‧‧Shell

4‧‧‧Sun gear

5‧‧‧Control housing

8‧‧‧ planetary gear

9‧‧‧Power transmission device

10‧‧‧First rotary bearing

11‧‧‧ Drive crank

14‧‧‧ crank arm

15‧‧‧ movable coupling

16‧‧‧Linear Guides

17‧‧‧ wall

18‧‧‧Second rotary bearing

19‧‧‧Sprocket

22‧‧‧ Third rotary bearing

23‧‧‧ rails

24‧‧‧Sliding parts

Claims (19)

A gear device for a system, wherein a guiding force is eccentrically introduced into a main shaft (1) of the gear device, the gear device comprising the main shaft (1), the main shaft (1) being relatively opposed by a main shaft bearing (3) Mounted rotatably on a fixed housing (2), wherein a sun gear (4) is concentrically disposed with the main shaft (1), the sun gear (4) is firmly connected to the housing (2), and Included is a control housing (5) that rotates about the housing (2), the first portion (6) of which is coupled to the main shaft (1) in a torsion-resistant manner, and a planetary gear (8) is coupled by a first A rotary bearing (10) is rotatably mounted on a second portion (7) of the control housing (5), the planetary gear (8) being engaged with the sun gear (4), wherein a force transmitting device (9) Is fixed to the control housing (5), a drive crank (11) is rigidly engaged with the planetary gear (8) by a first end (12) of the drive crank (11), wherein the drive A second end (13) of the crank (11) is rotatably mounted on a crank arm (14), and the crank arm (14) is coupled to the control housing (5) by a movable coupling Device (15) support, Characterized in that the movable coupling means (15) is a linear guide (16), absorbed by the tilting moment of the crank arm (14) delivered. A gear device according to claim 1, wherein the control housing (5) includes a wall portion (17) having an inner side surface (17a) facing the sun gear (4) and the planetary gear (8), and an outer side thereof (17b) faces the drive crank (11). The gear device of claim 1 or 2, wherein the crank arm (14) is mounted on the drive crank (11) by a second rotary bearing (18), and One end of the drive crank (11) is in contact. The gear unit of claim 2, wherein the linear guide (16) is mounted on an outer side (17b) of the wall portion (17). A gear device according to claim 1, wherein the force transmitting device (9) is at least one sprocket (19). The gear device of claim 1, wherein the linear guide (16) comprises at least one rail (23) configured with a slider (24) on which the slider (24) is guided . The gear device of claim 6, wherein the at least one guide rail (23) and the sliding member (24) are at least partially overlapped with the sprocket (19) or in the sun in the axial direction of the sprocket (19) The gear (4) direction is disposed behind the sprocket (19). The gear device of claim 6, wherein the at least one guide rail (23) or the sliding member (24) is at least partially overlapped with the sprocket (19) or in the sun in the axial direction of the sprocket (19) The gear (4) direction is disposed behind the sprocket (19). A gear device according to claim 6, wherein the at least one guide rail (23) is such that when the crank arm (14) makes one rotation, the slider (24) is on the intermediate shaft (x) of the main shaft (1) Set the way to travel twice. A gear device according to claim 6, wherein the slider (24) is movable on the guide rail (23) with one degree of freedom. A gear device according to claim 6, wherein two guide rails (23) are provided, wherein the slider (24) is movable on the two guide rails (23) with one degree of freedom. The gear device of claim 11, wherein the slider (24) is disposed at Between the rails (23), and by two pairs of rollers (25, 26) respectively supported on the rails (23), wherein the pair of rollers (25, 26) each comprise two rollers (27, 28) The shape of its cross-sectional profile is complementary to the cross-sectional profile of the associated guide rail (23). A gear unit according to claim 10, wherein a third rotary bearing (22) is engaged on the slider (24) and the crank arm (14). A gear device according to claim 6, wherein two guide rails (23) and two slide members (24) are provided. A gear unit according to claim 14, wherein each of the sliders (24) is movable on the associated rail (23) with one degree of freedom. A gear arrangement as claimed in claim 14, wherein each slider (24) is movable on the associated rail (23) with two degrees of freedom. The gear device of claim 14, wherein the sliders (24) are connected to each other by a transverse member (29), and a third rotary bearing (22) is disposed on the transverse member (29) and the crank Between the arms (14). The gear unit of claim 6, wherein the slider (24) is configured as a linear guide spherical ring member or a sliding bearing member. A gear device according to claim 1, wherein two control housings (5) are engaged on the main shaft (1), and the two control housings (5) are disposed to be offset from each other by 180 degrees in the circumferential direction.